CN113464624B - Gear shaping method for reducing gear tooth surface contact temperature - Google Patents

Gear shaping method for reducing gear tooth surface contact temperature Download PDF

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CN113464624B
CN113464624B CN202110751329.1A CN202110751329A CN113464624B CN 113464624 B CN113464624 B CN 113464624B CN 202110751329 A CN202110751329 A CN 202110751329A CN 113464624 B CN113464624 B CN 113464624B
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tooth
gear
modified
meshing
modification
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CN113464624A (en
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李发家
崔焕勇
刘吉宝
范士超
张少运
吴伟
杜金鹏
范启龙
杨国栋
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Shandong Menwo Transmission Co ltd
University of Jinan
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University of Jinan
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/17—Toothed wheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/08—Profiling
    • F16H55/0873—Profiling for improving axial engagement, e.g. a chamfer at the end of the tooth flank
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/08—Profiling
    • F16H55/088—Profiling with corrections on tip or foot of the teeth, e.g. addendum relief for better approach contact
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/10—Geometric CAD
    • G06F30/17—Mechanical parametric or variational design
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/20—Design optimisation, verification or simulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/08—Profiling
    • F16H2055/0866—Profiles for improving radial engagement of gears, e.g. chamfers on the tips of the teeth
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
    • G06F2119/08—Thermal analysis or thermal optimisation
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
    • G06F2119/14—Force analysis or force optimisation, e.g. static or dynamic forces

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
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  • Theoretical Computer Science (AREA)
  • General Physics & Mathematics (AREA)
  • Computer Hardware Design (AREA)
  • Evolutionary Computation (AREA)
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  • Mathematical Analysis (AREA)
  • Mathematical Optimization (AREA)
  • Pure & Applied Mathematics (AREA)
  • Gears, Cams (AREA)

Abstract

The invention relates to the technical field of gear shaping, in particular to a gear shaping method for reducing the contact temperature of the tooth surface of a gear, which comprises the following steps: s1: selecting tooth profiles corresponding to a three-tooth meshing area and a two-tooth meshing area which are closest to the tooth top as tooth profiles to be modified; s2: establishing a plane rectangular coordinate system (O-L) by taking an end point on the tooth profile to be modified, which is relatively far away from the tooth crest, as an origin OXΔ), the plane rectangular coordinate system (O-L)XΔ) ordinate axis LXParallel to the radial direction of the gear wheelThe abscissa axis of the rectangular plane coordinate system is a modification quantity delta; s3: calculating the maximum modification quantity delta of the end point of the tooth profile to be modified relatively close to the tooth topmax(ii) a S4: selecting a modification curve, wherein the equation of the modification curve is as follows:
Figure DDA0003146376660000011
in the above formula, LΔIs the ordinate of the end point of the tooth profile to be modified relatively close to the tooth top. The invention can reduce the highest tooth surface contact temperature when the gear teeth are meshed and reduce or even eliminate the sudden change of the load of each meshing area of the meshing gear.

Description

Gear shaping method for reducing contact temperature of gear tooth surface
Technical Field
The invention relates to the technical field of gear shaping, in particular to a gear shaping method for reducing the contact temperature of the tooth surface of a gear.
Background
At present, in the fields of automobiles, aviation, aerospace and the like, gear systems are developed towards high speed, heavy load and high precision. Higher requirements are made on the strength and the bearing capacity of the gear teeth. The bearing capacity can be improved by increasing the gear tooth module and lengthening the tooth width, but the volume power ratio of the gear transmission system is increased. The researchers of this part propose to increase the contact ratio of the gears to improve the bearing capacity of the gears, and refer to the spur gears with contact ratio larger than 2 as high contact ratio gears. After the contact ratio of the contact line of the tooth surface is increased, the total length of the contact line of the tooth surface is lengthened, the average load on the unit length is reduced, the large tooth height is the form which is commonly adopted by HCR gears, the tooth teeth of the HCR gears are lengthened, the relative sliding speed between the tooth spaces is increased, the frictional heat generation between the tooth teeth is increased, the instantaneous high temperature between the tooth surfaces tends to put forward higher requirements on the anti-gluing performance of the tooth surfaces, and the excessively high contact temperature causes the gluing of the gears. CN107255153A discloses a tooth crest trimming method for involute cylindrical gear with bearing capacity in gluing, which can prevent the gear from entering into engagement in advance due to deformation after long-time engagement, and reduce the hertz stress at the corner of the tooth crest when entering into engagement, but no solution is provided for how to reduce the highest temperature point (engagement point, engagement exit point) of gear engagement by trimming.
Disclosure of Invention
The invention aims to solve the defects of the prior art and provides a gear shaping method for reducing the tooth surface contact temperature of a gear, which reduces the highest tooth surface contact temperature when the gear is meshed by reducing the load of the highest point of the temperature of an unmodified gear and reduces or even eliminates sudden changes of the load of each meshing area of a meshed gear, thereby effectively improving the anti-gluing performance of the tooth surface.
The technical problem to be solved is realized by adopting the following technical scheme:
a gear shaping method for reducing the tooth surface contact temperature of a gear comprises the following steps:
s1: selecting tooth profiles corresponding to a three-tooth meshing area and a two-tooth meshing area which are closest to the tooth top on the gear tooth as tooth profiles to be modified;
s2: establishing a plane rectangular coordinate system (O-L) by taking an end point on the tooth profile to be modified, which is relatively far away from the tooth crest, as an origin OXΔ), the plane rectangular coordinate system (O-L)XΔ) ordinate axis LXThe abscissa axis of the plane rectangular coordinate system is a modification quantity delta parallel to the radial direction of the gear;
s3: calculating the relative position of the tooth profile to be modifiedMaximum profile modification delta near the tip end of the tooth tipmax；
S4: selecting a modification curve, wherein the equation of the modification curve is as follows:
Figure BDA0003146376640000021
in the above formula, LΔIs the ordinate of the end point of the tooth profile to be modified relatively close to the tooth top.
The technical scheme of the invention is as follows: in the step S3, ΔmaxAnd determining according to the stress deformation of the gear teeth, the base pitch deviation and the tooth form tolerance of the gear teeth machining.
The technical scheme of the invention is as follows:
Δmax＝δ+fm
in the above formula, δ is the comprehensive deformation of the tooth top of the gear tooth, including the deformation of the tooth top and the tooth bottom of two gear teeth at the initial meshing point; f. ofmThe calculation formula is that the machining error of the gear teeth is as follows:
Figure BDA0003146376640000022
in the above formula, fpbIs the base section error; f. offIs a tooth profile tolerance.
Compared with the prior art, the gear shaping method for reducing the contact temperature of the gear tooth surface has the beneficial effects that: (1) according to the tooth surface gluing flash temperature principle, the tooth profile of the highest temperature point (namely a meshing point and a meshing point) calculated by a gear theoretical formula is selected as the tooth profile to be modified, the relative sliding speed of the gear teeth at the point is high, the load is changed from zero, and the load is in direct proportion to the contact temperature. (2) DeltamaxThe magnitude of the tooth flank temperature of the meshing point is influenced,the method determines delta according to the stress deformation of the gear teeth, the base pitch deviation and the tooth profile tolerance of the gear teeth processingmaxThe pressure applied when the gear teeth at the engaging and disengaging point are engaged is reduced to zero, and the temperature at the engaging and disengaging point is reduced to the lowest.
Drawings
FIG. 1 is a schematic view illustrating a gear tooth profile modification according to an embodiment.
FIG. 2 is a schematic diagram illustrating the distribution positions of the three-tooth meshing area and the two-tooth meshing area of the first gear according to the first embodiment.
FIG. 3 is a schematic view of the engagement of a high contact ratio gear according to an embodiment.
FIG. 4 is an equivalent elastic model of the two teeth after the modification according to the first embodiment.
FIG. 5 is an equivalent elastic model of the modified three-tooth meshing according to the first embodiment.
FIG. 6 is a graph of load sharing rate along the tooth surface before and after dressing according to one embodiment.
FIG. 7 is a graph of the profile of tooth flank contact temperature before and after modification according to one embodiment.
In the figure: 1. the tooth profile to be modified comprises a gear tooth, 2, a tooth profile to be modified, 3, a modification curve, 4, a three-tooth meshing area, 5, a two-tooth meshing area, 6, a driving gear, 7 and a driven gear.
Detailed Description
The following examples are further illustrative of the present invention, but the present invention is not limited thereto. The present invention is relatively complicated, and therefore, the detailed description of the embodiments is only for the point of the present invention, and the prior art can be adopted for the present invention.
The first embodiment is as follows:
fig. 1 to 7 show a first embodiment of the present invention.
A gear shaping method for reducing the tooth surface contact temperature of a gear comprises the following steps:
s1: selecting tooth profiles corresponding to a three-tooth meshing area 4 and a two-tooth meshing area 5 which are closest to the tooth top on the gear tooth 1 as a tooth profile 2 to be modified;
s2: establishing a plane rectangular coordinate system (O-L) by taking the end point of the tooth profile 2 to be modified, which is relatively far away from the tooth crest, as an origin OXΔ), said planeRectangular coordinate system (O-L)XΔ) ordinate axis LXThe abscissa axis of the plane rectangular coordinate system is a modification quantity delta parallel to the radial direction of the gear;
s3: calculating the maximum modification quantity delta of the end point of the tooth profile 2 to be modified relatively close to the tooth topmax；
ΔmaxThe deformation of the gear teeth 1 is determined according to the stress deformation of the gear teeth and the base pitch deviation and the tooth form tolerance of the gear teeth processing, specifically,
Δmax＝δ+fm
in the above formula, δ is the comprehensive deformation of the gear tooth top, including the deformation of the gear tooth top and gear tooth bottom at the initial meshing point; when delta is equal to the sum of the maximum deformation of the tooth tops and the tooth bottoms of the two gear teeth at the initial meshing point, the optimal compensation amount for reducing the tooth surface contact temperature is considered; f. ofmThe calculation formula is that the machining error of the gear teeth is as follows:
Figure BDA0003146376640000041
in the above formula, fpbIs the base section error; f. offIs a tooth profile tolerance.
S4: selecting a modification curve 3, wherein the equation of the modification curve 3 is as follows:
Figure BDA0003146376640000042
in the above formula, LΔIs the ordinate of the end point of the tooth profile to be modified relatively close to the tooth top.
As shown in fig. 1, in the tooth profile modification method for reducing the tooth surface contact temperature of a gear in the embodiment, the tooth profile of the meshing tooth profile is modified to be composed of a modification curve 3 and a part of involute, and the modification of the gear is to modify the tooth crest parts of a driving gear 6 and a driven gear 7. In fig. 1, the broken line is the tooth profile 2 to be modified, and the solid line is the modified tooth profile.
The distribution of the meshing zones of the teeth 1 is shown in figure 2. The tooth profile 2 to be modified is determined according to the size of each meshing zone, the tooth profile 2 to be modified of the straight-tooth cylindrical gear with high coincidence ratio in the embodiment is the sum of a three-tooth meshing zone ac section closest to the tooth top and a two-tooth meshing zone ce section, the three-tooth meshing zone 4 is a tooth profile meshing zone with three gear teeth 1 meshed simultaneously, and the two-tooth meshing zone 5 is a tooth profile meshing zone with two gear teeth 1 meshed simultaneously.
As shown in fig. 3, when the gear is not deformed and the stressed gear is transmitted without error, the tooth pairs in the two-tooth meshing zone 5 and the three-tooth meshing zone 4 are in a simultaneous meshing state, and the deformation amounts along the meshing line direction are equal. After the gear teeth are modified, because the tooth profile at the tooth tops is reduced, the BE tooth pairs are firstly contacted in the AD, BE and CF tooth pairs during three-tooth meshing, and when the deformation of the BE tooth pairs reaches the modification quantity for compensating the AD and CF teeth, the AD and CF tooth pairs are contacted, because of the influence of tooth profile modification, the deformation between the engaged tooth pairs is not equal, and the load borne by the tooth pairs with large deformation is correspondingly increased. In this way, the load to which the engagement point and the disengagement point are subjected is reduced, so that the maximum tooth flank contact temperature during engagement of the gear teeth 1 is reduced.
As shown in FIG. 2, the comprehensive modification quantity of the driving gear and the driven gear corresponding to the ac, ce, eg, gi, ik sections of the meshing area is defined as CaH31、CaH21、CaH32、CaH22、CaH33。
By simplifying the gear teeth 1 into cantilever beams, the external load F borne by each meshing point of the gear teeth 1 is calculatedtThe load ratio of each meshing point of the gear teeth in normal meshing can be obtained through the deformation of the gear teeth. The calculation of the deformation and stiffness of the gear teeth has been carried out in a number of papers, for example, Levens, high contact ratio planetary gear train strength and dynamics research [ D ]]Nanjing, Nanjing university of aerospace 2015.
When the teeth are engaged, the external load F is as shown in FIG. 4tComprises the following steps:
Ft＝FADⅠ+FBEⅠ
when two teeth are meshed during HCR gear meshing, a stress deformation formula is shown as the following formula.
δⅠ1＝δⅠ2+ΔⅠ1
FADⅠ＝CADⅠδⅠ1
FBEⅠ＝CBEⅠδⅠ2
Simultaneous upper type get
Ft＝CADⅠδⅠ1+CBEⅠδⅠ2＝(CADⅠ+CBEⅠ)δⅠ1-CBEⅠΔⅠ1
By making F out of the formulatExpression for calculating single tooth bearing force FADⅠ。
Figure BDA0003146376640000051
By the same token
Figure BDA0003146376640000052
According to the tooth surface meshing change after the actual tooth profile modification, the tooth top modification on the driven gear tooth 2 is equivalent to the modification on the tooth root on the driving wheel 1, so that the delta is modifiedⅠ1Equivalent substitution is as follows:
ΔⅠ1＝CaH22-CaH21
bringing into availability:
Figure BDA0003146376640000061
Figure BDA0003146376640000062
in the above formula, FtAn external load on the gear teeth 1, FADⅠ、FBEⅠLoads borne by AD, BE tooth pairs, CADⅠ、CBEⅠUnit tooth width mesh stiffness, Δ, of AD and BE tooth pairs, respectivelyⅠ1、ΔⅠ2For the difference in deformation between the zones of engagement, δⅠ1、δⅠ2Are respectively asThe amount of deformation of the two pairs of teeth.
As shown in fig. 5, when the three teeth are engaged, the force deflection of each tooth pair per unit tooth width is listed:
δⅡ2＝-ΔⅡ1+ΔⅡ2+δⅡ3
δⅡ1＝ΔⅡ2+δⅡ3
FADⅡ＝CADⅡδⅡ1
FBEⅡ＝CBEⅡδⅡ2
FCFⅡ＝CCFⅡδⅡ3
when the three teeth bear load, the external load is as follows:
Ft＝FADⅡ+FBEⅡ+FCFⅡ
the formula above can be combined to obtain:
Figure BDA0003146376640000063
Figure BDA0003146376640000071
ΔⅡ1＝CaH31-CaH32
ΔⅡ2＝CaH33-CaH32
Figure BDA0003146376640000072
the same principle is that:
Figure BDA0003146376640000073
Figure BDA0003146376640000074
in the above formula, FtAn external load on the gear teeth 1, FADⅡ、FBEⅡ、FCFⅡLoads borne by AD, BE, CF tooth pairs, respectively, CADⅡ、CBEⅡ、CCFⅡUnit tooth width mesh stiffness, Δ, for AD, BE, CF tooth pairs, respectivelyⅡ1、ΔⅡ2For the difference in deformation between the zones of engagement, δⅡ1、δⅡ2And deltaⅡ3The deformation amounts of the three pairs of teeth are respectively.
Further analyzing the change condition of the load on the meshing line after the modification, obtaining the load distribution of each point on the meshing line according to the load formula of each modified meshing point when the two teeth are meshed with the three teeth, and obtaining a graph 6 by using MATLAB (matrix laboratory) to map the calculated data of each meshing point, wherein the load change is more visual and is represented by load sharing rate, and the load sharing rate is the percentage of the load of a certain gear tooth at the meshing point to the total load. The gear tooth 1 is shaped, compared with the original unmodified tooth profile, the load change of each meshing area is stable, the tooth top deformation of the gear tooth is zero after modification, no stress is applied during meshing, the load sharing rate of a meshing point and a meshing point changes from zero, the meshing and meshing impact is eliminated, and the maximum contact temperature point of the unmodified gear is reduced to the minimum. According to the calculation of the bonding bearing capacity of the cylindrical gear in the national standard GB/Z6413.1-2003, the contact temperature of each meshing point can be calculated. By utilizing MATLAB to plot according to temperature data points, the result is shown in figure 7, and compared with the tooth surface contact temperature calculated according to a flash temperature method before and after the modification, the highest tooth surface contact temperature during gear tooth meshing is reduced, and the total heating value of gear tooth meshing is reduced, so that the modification method can obviously improve the tooth surface contact temperature and improve the gluing resistance and bearing capacity of the gear.
The embodiments of the present invention have been described in detail with reference to the accompanying drawings, but the present invention is not limited to the above embodiments, and various changes can be made within the knowledge of those skilled in the art without departing from the gist of the present invention.

Claims (1)

1. A gear shaping method for reducing the tooth surface contact temperature of a gear comprises the following steps:
s1: selecting tooth profiles corresponding to a three-tooth meshing area (4) and a two-tooth meshing area (5) which are closest to the tooth top on the gear tooth (1) as tooth profiles (2) to be modified;
s2: establishing a plane rectangular coordinate system (O-L) by taking the end point of the tooth profile (2) to be modified, which is relatively far away from the tooth crest, as an origin OXΔ), the plane rectangular coordinate system (O-L)XΔ) ordinate axis LXThe abscissa axis of the plane rectangular coordinate system is a modification quantity delta parallel to the radial direction of the gear;
s3: calculating the maximum modification quantity delta of the end point of the tooth profile to be modified relatively close to the tooth topmax，ΔmaxAccording to the stress deformation of the gear teeth and the base pitch deviation and tooth form tolerance of the gear teeth processing,
Δmax＝δ+fm，
in the formula, delta is the comprehensive deformation of the tooth tops of the gear teeth (1), and comprises the deformation of the tooth tops and the deformation of the tooth roots of two gear teeth at the initial meshing point; f. ofmThe calculation formula is that the machining error of the gear teeth is as follows:
Figure FDA0003660734480000011
in the above formula, fpbIs the base section error; f. offIs a tooth profile tolerance;
s4: selecting a modification curve (3), wherein the equation of the modification curve (3) is as follows:
Figure FDA0003660734480000012
in the above formula, LΔIs the ordinate of the end point of the tooth profile (2) to be modified relatively close to the tooth top.
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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3937098A (en) * 1974-11-18 1976-02-10 Rouverol William S High torque gearing
CN107025367A (en) * 2017-06-05 2017-08-08 太原理工大学 Spur gear wheel profile modification method based on gear teeth thermoelastic distortion and gear diagonal distortion
WO2020252843A1 (en) * 2019-06-19 2020-12-24 江苏太平洋精锻科技股份有限公司 Bevel gear tooth surface point-to-point modification method suitable for forging process

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3937098A (en) * 1974-11-18 1976-02-10 Rouverol William S High torque gearing
CN107025367A (en) * 2017-06-05 2017-08-08 太原理工大学 Spur gear wheel profile modification method based on gear teeth thermoelastic distortion and gear diagonal distortion
WO2020252843A1 (en) * 2019-06-19 2020-12-24 江苏太平洋精锻科技股份有限公司 Bevel gear tooth surface point-to-point modification method suitable for forging process

Non-Patent Citations (10)

* Cited by examiner, † Cited by third party
Title
EQ140-1700C变速箱汽车齿轮的修形设计及加工;裘俊彦;《河海大学常州分校学报》;20071215(第04期);全文 *
SS8-Ⅱ型机车牵引齿轮的修形降噪设计;汤兆平等;《科学技术与工程》;20160318(第08期);全文 *
工程机械齿轮的修形设计与加工;崔传勋;《机械传动》;19960930(第03期);全文 *
按齿轮刚度理论进行齿廓修形及其加工方法;辛经纬;《上海工程技术大学学报》;20090315(第01期);全文 *
直齿轮传动误差激励分析与齿廓修形曲线设计;刘红旗等;《机械传动》;20151215(第12期);全文 *
考虑轴线平行度误差及热变形的齿轮修形设计;杨欣茹等;《机械传动》;20161015(第10期);第74-79、101页 *
高速齿轮传递误差和啮入冲击的激励模拟及齿面优化修形;贾超等;《振动与冲击》;20191215;第38卷(第23期);第103-109、138页 *
齿廓修形对渐开线直齿轮设计传递误差的影响;陈洪月等;《华中科技大学学报(自然科学版)》;20180323;第36卷(第03期);第91-97、132页 *
齿轮修形小结;张玉梅等;《橡塑技术与装备》;20071015(第10期);全文 *
齿面微观修形技术在齿轮降噪中的应用;张福龙等;《机械强度》;20130815(第04期);全文 *

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